Balanced double-acting engine



April 5, 1949. F. MERCIER EI'AL 2,466,255

BALANCED DOUBLE- ACTING ENGINE Filed Oct. 27, 1942 i s Sheets-Sheet 1 Pzkrre frnesz 448/00 81 [/77652 Frederic Ale/"(fer INVENTORS ATTORNEYS April 5, 1949. E. F. MERCIER ETAL BALANCED DOUBLE-ACTING ENGINE 6 Sheets-Sheet 2 Filed Oct. 27, 1942 l x A u ill/ ATTORNEYS April 5, 1949. E. F. MERCIER EI'AL. 2,466,255

BALANCED DOUBLE-ACTING ENGINE Filed Oct. 27, 1942 s Sheets-Sheet :5

. 1NVENTORS Pzerre [rnest Meraer 8 [rmvt fade/it Ale/"ever m,mw

A TTORNE XS April 5, 1949. E. F. MERCIER arm.

BALANCED DOUBLE-ACTING ENGINE Filed Oct. 27, 1942 6 Sheets-Sheet 4 INVENTORS BY 644 9' 6r.

ATTORNEYS April 5, 1949. F. MERCIER EI'AL 2,456,255

BALANCED DOUBLE-ACTING'ENGINE Filed 001 27, 1942 I 6 Sheets-Sheet 5 frame frederic Mere er INVENTORS BY held nz, fai &

ATTORNEYS April 5, 1949. E. F; MERCIER ETAL BALANCED DOUBLE-ACTING ENGINE 6 Sheets-Sheet 6 Filed Oct. 27, 1942 Pierre [urea-z? Marc-[er &

frnesz free/era Mercz'er INVENTORS ATTORNE Y5 Patented Apr. 5, 1949 2,466,255 BALANCED DOUBLE-ACTING ENGINE Ernest Frederic Mercier, Eguzon,

France, and

Pierre Ernest Mercier, New York, N. Y.

Application October 27, In France Nov 1942, Serial No. 464,433 ember 23, 1940 Section 1, Public Law 690, August 8, 1946 Patent expires November 23, 1960 The present invention relates to improvements in prime mover apparatus and especially to a gas generating and air compressor apparatus. The invention relates more particularly to a combination including a balanced double-acting internal combustion engine and air compressing means which cooperate to supply hot compressed gases which may be used in a gas turbine, a gas propulsion nozzle or other prime mover.

A problem of long standing in the use of gas turbines has been the production in an economical manner of a dependable supply of highly compressed gases at a temperature low enough to avoid damage to the turbine blading or undue wear and maintenance problems in connection therewith, while at the same time conservin the heat energy of said gases so that it may be utilized to maximum effect in the turbine.

One of the principal objects of this invention is to provide an apparatus capable of supplying to a turbine or other prime mover, a mixture of compressed gases of regulated temperature and pressure while conserving the energy developed therein during the generating and compressing steps.

A further object of the invention is to provide a gas generating and compressor apparatus in which a plurality of internal combustion engine firing chambers are. provided as power and gas generating units and are connected together with their complementary moving parts disposed in balanced relation and cooperating to insure a maximum degree of freedom from vibration.

Still another object of the invention is to provide, in an apparatus of the class described, an arrangement whereby a plurality of firing chambers are so connected with one or more gas compressor units as to obtain an increased efficiency in the utilization of the power and heat energy developed in said firing chambers, while at the same time simplifying incidental operations such as control of flow of compressed gas to and through the firing chambers, cooling of the firing chambers, and feedin of fluid fuel thereto.

A still further object of the invention is to provide an apparatus of the class described which is characterized by compactness and light weight for a given power output and wherein many of the linkages, connecting rods, cranks, and other auxiliary elements necessary to the operation of conventional internal combustion engines and the transfer of their power to a driven machine are eliminated.

The above and other objects and advantages are obtained according to the invention by as- 3 Claims. (01. 123-46) balanced relation.

sociating one or preferably a plurality of sets of free pistons in open-ended firing cylinders so disposed with relation to one another and to a double-acting air compressor as to insure that the several pistons will move synchronously in In other words, the'arrangement is such that the essential elements partaking in the synchronous movements are so distributed between two opposing assemblies of the free pistons and the correlated elements of the air compressor that each movable member of one assembly will have in the other assembly a corresponding member movable in the opposite direction. In this way thrusts and counterthrusts which in prior constructions are transmitted to stationary supporting members are neutralized without loss of energy from the system. but instead such energy is transferred to the air undergoing pressure in the system and which is ultimately discharged with and as a part of the gases passing from the firing cylinders.

The invention will now be described more particularly with reference to the accompanying drawings, wherein similar reference characters designate similar parts throughout the respective views:

Figs. 1 and 2 respectively are diagrammatic views in longitudinal section of two forms of gas generating and compressing assemblies embodying certain of the broader principles of the invention;

Fig. 3 is a longitudinal section of another modified form of the invention;

Figs. 4 and 5 are longitudinal sections of a further modified form of the invention showing the same machine in two extreme positions;

, Fig. 6 is a diagrammatic view from the end of a six cylinder machine which otherwise may conform either to the structure of Fig. 4 or Fig. 5';

Fig. 7 is a diagram showing still another disposition of the firing cylinders;

Fig. 8 is a view in longitudinal section of another modification of the invention;

Fig. 9 shows two transverse half-sections taken respectively along th lines A-A and B B of Fig. 3;

Fig. 10 is a partial tion, of a variation of inders of Fig. 3, and

Figs. 11 and 12 are diagrammatic views showing the disposition of two assemblies in two different positions with reference to a hydraulic fluid fuel injector-operating means.

In the drawings, which are merely illustrative view, in longitudinal secone of the compressor cylplant designed to promote economy of space and fuel consumption. A characteristic feature of such power plant resides in the arrangement whereby the movable parts of the air compressors are connected for coordinated movement with the moving parts of the power and gas generating units, and in the grouping of these units into two opposing sets to permit imparting staggered strokes to the pistons of both groups.

There are various ways of accomplishing this. For example, Fig. 1 shows a type wherein a pair of open-ended engine cylinders l and 2 and a pair of compressors and 4 are arranged along one and the same axis with the two coaxial enline cylinders'disposed adjacent to one another. A double piston PP is mounted for reciprocation in the adjacent ends of the cylinders and coopcrates with pistons lb and 2b in defining the combustion chambers of the respective cylinders.

The pistons lb and 2b are respectively connected with pistons 3a and 4a and reciprocate the latter in their respective compressor cylinders which are arranged respectively at the outer ends of the engine cylinders. Fig. 2' shows a double acting compressor unit 5 which occupies the central position occupied by the adjacent engine cylinders in Fig. l. The double-acting piston 5a of the compressor has hollow extensions 5b extending on each side of the piston toward the cylinders 6 and 1 and these extensions are connected to pistons 6a and 1a disposed in the cylinders.

Figure 3 shows a pair of double acting compressor cylinders 40 and 4| arranged in spaced relation and mounted for movement axially'as a unit. Combined therewith are two sets of cyle linders 32' and 33', only one cylinder of each set being shown in Figure 3, the two cylinders being arranged in .opposed relation,- the sets being distributed as shown in Fig. 9 around the longitudinal axis of the compressor intermedi ate the compressor cylinders and cooperating with pistons 34, 35, 6! and 62 reciprocating within the ends thereof to form firing chambers.

Figure 4 shows a plurality of,adjacent internal combustion cylinders, arranged about a common central axis and all of which are connected'so as to actuate a double acting compressor, located laterally of the cylinders on the central axis. The difference between the disclosures of'Fi ures 3 and 4 is this: In Figure 3, there are compressor cylinders at each end of the ma- 4 same disposition of motor cylinders as Figure 4, there are two coaxial sets of compressor assemblies cooperating therewith instead of one. The advantage of division of the power of the motor cylinders thus obtained finds. particular application to Diesel engines in which the i8- nition speed of the fuel atomized is limited so that large bulky cylinders cannot be used.

In Figures 4 and 5, the entire series of motor cylinders are arranged into .two groups, the cylinders of one group alternating with respect to those-of the other group. In Figure 7, this arrangement is shown diagrammatically where it will be seen that one group of cylinders C C", C etc. alternate between another group C' 1, 0'2, and 0'3, all of the cylinders being arranged in a circle so that the various cylinders making up the two internal combustion engines are situated in a plane perpendicular to the direction of the common axis of such engines. Each cylinder has a pair of oppositely arranged pistons which are unconnected to each other and are adapted to reciprocate in the open ends of the cylinder.

. Six engine cylinders are contemplated in Figcompressed air conduit to feed the cylinders with compressed air.

It is proposed to give the pistons of one group a staggered stroke with respect to those of the other group so that while the one group perform theirpower stroke the other group will perform their compressor stroke, and vice versa.

The arrangement is such that all the pistons of one group I, at one and the same end of their cylinders are constrained to move in a direction counter to all the pistons of the other group 2 which are at the same end of their cylinders as the first group. This is also true of the two groups of pistons I and 2 which are disposed at the other end of the foregoing two groups of cylinders. These groups of pistons will move in opposite directions In, Figures 4 and 5, when the oppositely arranged pistons 3 and 4' are completely within their respective cylinders after having completed their compression stroke, the oppositely arranged pistons 3 and 4 of adjacent cylinders are projected beyond the opposing ends of their cylinders, having completed their expansion stroke. -In other words, pistons 3' and 4' disposed in one of the cylinders respectively move in one and the same direction as pistons l and 3, disposed in the alternate cylinders at the opposite ends thereof. Hence when pistons 4 and 3, of one cylinder of one group follow their compression stroke, pistons 4" and 3' of the other cylinder follow their expansion stroke, there bepistons with one piston of a cylinder of one set in coaxial alignment with the piston. of '9, 'cyl-"' inder of the second setthis arrangement be-1 ing true of the succeeding pairs of aligned cyl-.

inders in the various positions circumferentially in these two sets. But in Figure 4, one half of p the total number of cylinders of a circular set ing one power impulse for each stroke.

-'I'he means for actuating these pistons to impart the foregoing- -movements consists of the -movable-parts, ofthe compressor device and their connections. The engine cylinders are fixed in 'position andproject through an annular closed fluid admission jacket 15. Slidably projecting concentrically in saidjacket is a tubular conduit Figure 8 discloses a still further departure from the foregoing in that, while it shows'ithe 9 which serves as a piston rod. The six engine cylinders are coupled to a single compressor device to provide a unitary generator, the circle circumscribed by the cylinders being preferably of a inder, ll. I

hollow piston II is carried by tube 9 short of one.

end and traverses snugly in the compressor cylinder l4. A series of vent ports A is formed in one disk l8 and another series B formed in the other .disk l. .Check valves C control vents A and check valves D control vents B. In hollow piston I I on one wall are check valve controlled vents E and on the other wall are check-valve controlled vents F. This hollow piston communidates with bore of tube 9 by means of a port I2, and tube 9 communicates with jacket is by means of ports l3.

A yoke or saddle piece 8. encircling tube 9 has pivotal connections with three pistons 4 of one group I, which are on the same side of jacket I5, being connected rigidly peripherally of said jacket by connecting rod to the end wall I0 of compressor cylinder l4. The pistons 4 of the'other group, which are on the same side of jacket l5 as pistons 4', are pivotally connected to a yoke 6 carried by tube 9 at one end thereof.

The pistons 3' of the group on the other side of jacket l5 which are in the same cylinders with pistons 4' are pivotally secured to a yoke fixed on tube 9 at a point intermediate its ends. Finally the pistons 3 of the second group on the said other side of jacket l5 which are in the same cylinders as pistons 4 are pivotally connected to the terminals of link rods 5 the inner ends of which are secured to the end Wall I0 of compressor cylinder I4.

This construction of intercoupled motor and compressor assemblies assures that every element comprised in each of the two moving bodies has in the other moving body a'corresponding element geometrically identical and subject (in the opposite direction) to exactly the same pressures, in normal or in abnormal operation. It is obvious that, if desired, the median planes of all the motors, instead of coinciding as in the example described in the preceding text can be arranged parallel and in spaced relation, this requiring, however, lengthening of the machine.

The same underlying principle of construction can be adapted in connection with providing a two-stage compressor for feeding internal combustion cylinders with compressed air at a high pressure, say at a pressure from 8 to kilograms.

cating directly with jacket |5. In the main length of tube 9 is fixedly positioned, a cooler device for the air, the inlet and outlet water passages of which extend into reduced end 9A of this tube and slidably project through stuifing boxes located in the adjacent closed end 33 of this tube.

The compressor-cylinder 6 of the low pressure stage is disposed concentrically of tube 9,

being provided with check-valve controlled vents H. Slidably closing one end of this cylinder I6 is a hollow piston wall |8 carrying exhaust valves 21 controlling adjacent vents which communicate with the interior of a high pressure cylindrical 6 chamber between which and cylinder l8 is the annular cylindrical space 29. Chamber I1 is attached at one end to movable piston wall l8 and at its opposite end is attached to and closed by another hollow piston wall l9 also slidable in cylinder IS. The hollow space of first piston |8 communicates with the annular space 29 by means .of cylinder 4 I.

of ports 28, which annular space, in turn, communicates with pipes 24 which establish linesof flow of compressed fluid directly into the jacket l5.

Also slidably positioned in cylinder I6 is a piston 20 spaced a convenient distance from hollow piston IS in fixed relationship thereto. It will be seen that connecting rods 5, which connect piston l8 to yoke B'that operate piston 4' is made of a length suitable to simultaneously interconnect the hollow pistons I8 and I9 as well as the solid piston 20 so all three pistons will move at the same time along tube 9, carrying cylindrical high pressure chamber ll along with them.

Hollow piston wall l9 has vent ports 28 which communicate with theinterior of the annular space 29. The wall l9 also carries exhaust valves 21 controlling ports that communicate through the hollow wall l9 and the ports 28 with the interior of the cylindrical jacket N. This hollow piston wall I9 divides the high pressure from the low pressure zone of the multi-stage compressor. The hollow piston 2| of the low pressure zone is keyed onto tube 9 and makes a traverse between hollow piston l9 and solid piston 20, both slidable in cylinder I6. This hollow piston 2| has check valve controlled ports S on one side wall and check valve controlled ports T on its opposite wall. Communication between hollow piston 2| and tube 9 is had by means of ports 26 formed in this tube 9 in a plane with said piston. A smaller hollow piston 22 is also keyed to tube 9 and has a traverse in cylindrical chamber It has, on one wall, check-valve con trolled ports M and on its opposite wall checkvalve controlled ports 0 both sets of ports communicating with the interior of cylindrical chamber respectively at opposite sides of piston 22.

In the device just described, the pistons operate in two adjacent compartments, one being the high pressure chamber one piston, 22, of the pair of pistons carried by tube 9 operating in the chamber ll, while the other piston, 2|, operates in the other low pressure compartment. It will be seen that tube piston 2| slides relatively to and over connecting rod 5.

In Fig. 3, the compressor cylinders 48 and 4| are supported at their adjacent sides by the tube 3'! which is arranged concentrically of a shaft 3| and is supported for sliding movement in the closed cylindrical jacket or air chamber 5|; The tube 31 fixedly carries at one end a hollow piston 38 and .a similarly fixed hollow piston 39 at the other end. Piston 38 is adapted to make a stroke in compressor cylinder 40 between oppositely inclined walls 42 and 43. Piston 39 similarly moves between the oppositely inclined walls and 45 A rigid connecting rod 46 is attached at opposite ends to end walls 43 and 45, respectively, of cylinders 40 and 4|.

One wall of each piston 38, 39 carries pressure valves 48, while the other wall carries check valves W. The wall 42 of the cylinder 40 facing the valves 48 of piston 38 carries check valves Y while that wall 45 of cylinder 4| which faces valves 48 of piston 39'carries check valves 4|.

-The compressor pistons 38, 39 connect with the interior of tube 3|v by means of passages 49 and compressor assemblies disclosed in this figure.

when either rack moves in one direction it will rotate the pinions, causing these pinions in turn to move the other rack in a 'oounter direction. The racks and pinions also give central support to the movable tube 31.

As previously mentioned, two seriesof firing cylinders are arranged in circular rows around tube 31, with the adjacent ends of the cylinders of the two rows projecting into the jacket 5| as shown in Figs. 3 and 9. The cylinders of the two sets are'disposed in horizontal, coaxial alignment with one another, two of such cylinders 32 and .33 being shown in Fig; 3. A pair of oppositely movable pistons 62 and 34 move in cylinder 32' while a similar set designated 61 and 35 move in cylinder 33. The pistons 62 and '6! at the opposite ends of the aligned cylinders are connected for linear movement to cylinder walls 43 and 45, respectively,. of cylinders 40 and 4| by short links 34 and G3.- The-inner pistons 34 and 35 moving in these same cylinders are connected together for joint movement by a common piston rod 35b to which is'attached centrally the yoke 36, which in turn is secured to the tube 31.

It will thus be seen that in this construction of parts, provision is made for moving the compressor pistons carried by the central tube 31 in one directionof reciprocation in their encasing compressor cylinders, while, at the same timefimeans are provided for reciprocating these compressor cylinders relatively to the tube in a counter direction. As a result the end walls .of the cylinder behave as pistons in cooperating with the compressor pistons 38 and 39, moving towards or away from the pistons 38 and 39 associated with them, and regardless of the direc-- At the center of the length of each' cylinder 32', 33' as shown in Figure 3 is the inlet port I for the fluid fuel coming from the injector 83 or 83'. On the opposite sides ofeach inlet port I along the length of each cylinder are ports 52 and 53 defining admission and exhaust passages, respectively, for reception of compressed air and for exhausting the combustion gases. Between the exhaust ports 53 and the injector inlet ports I are relatively restricted supplementary or auxiliary exhaust ports 55. A pair of valvular sleeves tion of reciprocation, compressing air in the spaces between the pistons and the compressor cylinder walls mthat stage of the cycle when theyare approaching-one another; As the compression reaches the desired-value -.determincd by the setting 1 the vagin -"mas may be, thwe valves respectl panand e osc permitting the compressed 11w into, the

tube 31 and thence through the openings 53 to the central chamber 5|.

As the tube 31 is moved back and forth con comitantly with movement ofthe pistons 34 and 35, the cylinders 40 and 4| are moved in the opposite direction to tube 31 ineach stroke of said tube 31 by virtue of the movement imparted to the cylinders 40 and 4| through the short links 53am! 64 and the rigid connecting rod 46. It

will be understood from the. above description that in each such stroke, both of thetubcs 31 I and the .pistons 38 and 39 .carried thereby and of the cylinders 40 land 4|, a power impulse is 55 and 55a, mounted for limited sliding movement along the cylinders 32 and 33, serve respectively to control the covering and uncovering of the ports 56 of both cylinders in synchronism with the movement of the pistons. The inner parts of these sleevesmove, piston-like, in annular chambers 51 surrounding the cylinders and bored out of the adjacent cylinder frames, the latter being provided with exhaust outlets 54 and 54a with which the exhaust passages 53 and ports 56 communicate. The two sleeves 55 and 55a are coupled together for conjoint movement by a tie rod 59. It will be seen that when the tube compressor pistons 38 and 39 are positioned, as shown in Figure 3, their greatest distance apart from the walls 42 and 45 of compressor cylinders 48 and, pistons35 and 6| in cylinder 33 will be positioned in close proximity at the center thereof, while pistons 62 and 34 in cylinder 32 will be separated their greatest distance apart.

Similarly in Figures 4 and 8 pistons 3', 4, in

. one cylinder there shown will be positioned in close proximity, while pistons 3 and 4 of the other cylinder shown will be separated their greatest distance apart. In these figures the valves or valvular sleeves which control the admission of fluid to,'as well as exhaust of fluid from the cylinders may be synchronously operated by any desirable means, not shown.

Supplying the cylinders shown in Figure 3 with hot fuel gases or other-fluid fuel isdone by any desirable means. as is also regulation of the intervals of injection. As one way to accomplish this function we disclose; a hydraulically operated mechanism for actuating an injector or injectors which feed hot fuel gases into thefiring' cylinders.

Two injectors 83 ,and'83' are provided for the tafgleylinders shown in Figure 3. Poppet valves Ila, Figs. 9, 11 and 12, move in the fuel dnjoctors and are controlled in the conventional way by springs (not shown). Reference being made to Figure 11, it will be seen that when poppet valve Bla is closed, pistons 62 and 34 have been completing their expansion stroke, while poppet valve Bla' has opened to admit hot gases in order to impel pistons 35 and BI outwardly in a corresponding expansion stroke. A pair of rack rings 8") and 810 are operably mounted for oscillatory movement around cylindrical jacket 5!? given thereto produced by the combustion of the fuel alternately in the cylinders 32""and 33'.

The means provided for imparting to the oppositely arranged pistons of cylinders of the two groups afull free expansion stroke and a partial, interrupted compression stroke is shown by .ljigure 3 to be adapted to the type of ,motor An"aocurate series of teeth M are formedperipherally of each ring Adapted to mesh with the teeth on the rings are rack-bars 86 attached to an actuating piston 81 operating in cylinder 81a, and rack-bar 86' attached to piston 81 operating in cylinder 8'"). Rocker arms Bland 84' are pivoted so as to present each a roller '8ld opposite ring 31p and ring tile. The outer ends of the rocker engage the outer ends of the poppet valves Bid and any which control the flow of fluid fuel through the injectors.

Fixedly disposed at the opposite ends of jacket 5| are a pair of cylinders I05 and a in which operate pistons N and N having tubular piston rods P and P closed at their points of attachment to the adjacent walls 49 and 45 respectively of compressor cylinders 49 and 4| respectively. There are fixed tubes D, D, extending C' connects inner end of cylinder |a with the cylinder 81b. Pipe C also connects with a pump 9| which connects by pipe 9| to an accumulator cylinder 90, while pump 9| has a pipe 92 which connects it to sump 92. Similarly pipe C has the connection to a pump 9|, which pump has a pipe 92' extending from a sump 92 and also a pipe 9| which connects to an accumulator cylinder 90.

Oil or any other suitable fluid fills each cylinder I05, "15a, but not at the same time. In Figure 3 at S is shown a port in tube D, just in advance of the final outer position in which piston N has moved; similarly tube D' in cylinder IBM has a similar port S in the same relative position. When the pistons N, N are in the positions shown in Figures 3 and 11, piston rod N and its tubular piston P are encased by cylinder W511 and there is no oil in this cylinder. In

cylinder 81a piston 81, Figs. 9 and 11, is in down position when piston N is in the position at the left in cylinder I05 and there is oil F in the bottom of cylinder 8117 whose piston 81' is at the top end of this cylinder.

It may be desirable to cushion the hollow pistons 38 and.39 as they reach the end of their stroke in the compressor cylinders in either direction. In Figure 10 are disclosed the details. An annular flange 98' extends outwardly from the wall 96 of the compressor cylinder 49 and cooperates with an inner spaced concentric band H in defining an annular chamber 91 closed at its outer end but communicating at its inner end with the interior of the compressor cylinder 49. There is a piston 98 movable in this chamber 9'lthe latter being reduced in width where it opens out into cylinder 49 and in this restricted annular orifice moves a flange 98a formed on piston 98. A compression chamber 99 is provided between piston 98 and the wall 96 of cylinder 40.

Check valves Y are carried by this wall. The band H. is formed with a series of ports I00 which communicate with compression chamber 99.

I will now describe the operation of the machine, in all of its varied forms.

Referring to Figure 4, the compressed air delivered by tube 9 from the compressor cylinder It has already been compressed in the chamber between inwardly-moved pistons 4' and 3' and reacts now, under influence of pressure, to move these pistons outwardly, and in doing so piston 3' moves to the right outwardly carrying yoke I with it, hence moving tube 9 to the right as shown in Figure 5, and as this tube moves by means of its yoke 6 it moves outwardly disposed piston 4 inwardly of its cylinder towards the right. But piston 4' is also moved outwardly of its cylinder towards the left, and as it moves, carries yoke 8 along with it, thus causing compressoroylinder l4 to move to the left, hence causing piston 3 to move towards the left inwardly or its cylinder. Pistons 9', 4' are making an expansion stroke while pistons 3, I thus make a compression stroke. As pistons 3', 4' expand compressed air is drawn in as indicated by the arrows, into admission ports T which have been opened by appropriate mechanism for this purpose. As pistons 8, 4 move towards each other, these admission ports T close. As'the pistons reach the end of their expansion stroke the fluid is exhausted out of ports U.

As tube 9 moves to the right and cylinder ll moves towards the left, hollow piston carried by tube 9 and end wall In carried by cylinder move away from each other, while piston II and end wall I0 move towards each other. In moving to the right air'is being sucked in by the ports controlled by valves A, which valves have opened because there is a suction being created in cylinder l4 between wall In and piston II. This is shown by arrows in Figure 5. The suction has closed valves E on piston II, but inasmuch as piston H is compressing air in cooperation with wall ID as they approach, valves F in piston II are opened so the air is forced into hollow piston II and injected by way of ports I 2 into tube 9 and thence it passes by way of ports l3 into jacket l5 and may be led off for any desired use. The valves A and F which opened during this stroke of piston II to the right, close when this piston moves in a counter direction shown in Figure 4, while the previously closed valves E are now open, and as pistons l0 and II are now compressing air, the latter enters into hollow piston I again and is ejected by tube into the jacket by the means just now set forth. The action of the movable parts of this compressor is thus double-acting.

Now the result of the movement of these parts is to stagger the strokes of the pairs of double pistons contained in the cylinders shown in Figures 4 and 5, which are arranged oppositely to each other. This is also true of the pistons shown in Figure 8. In this figure the compressed air delivered out of the compound high and low pressure compressor is cooled by the coils of radiator 23 where it passes through tube 9 enroute to the motor cylinders.

In Figure 8, the direction of movement of the mobile parts is as follows: pistons |8, I9 and 20 togetherwith cylinder I! are just completing their movement towards the left, while tube pistons 2| and 22 are completing their movement towards the right. In doing so pistons 2| and'2ll compress air, closing intake valves H in cylinder l6 until piston 2| has passed, thereby opening valves S and closing valves T in hollow piston 2|, causing compressed air to flow by way of ports 26 out of piston 2| into tube 9, to be cooled by radiator 23 on its way out to ports T into small hollow piston 22. Pistons 2| and I9 are separating so atmospheric air enters as valves H open after these pistons have passed thereon, this being the admission stroke in the low pressure area. As this takes place pistons l8 and 22 are also separating, as pistons 22 and I9 approach and are compressing air in cylinder l1, so a suction is created between pistons I8 and 22, andthe compressed air in hollow piston 22 which came out of hollow piston 2| rushes from piston 22, unseating check valves M and enters chamber I1, this being the admission stroke in the high pressure section or r-tagevalves 2'1 in piston I8 closing at this time. Now, as pistons 22 and I9 approach, the air they 11 compress causes valves in hollow piston 22 to close, so this compressed air is forced out of chamberzl'lthrough ports controlled by valves 21 in hollow piston It, as the latter have been forced open by theair-pressure. The compressed air is now driven out of hollow piston is through ports into the-annular space: 29 surrounding chamber or cylinder i1, and out through delivery pipes 24 into jacket I! for feeding the engine cylinders and also for any other useful purexpansive force, thereby driving pistons 35 and thence out of delivery pipes 24 to the-jacket l5 for further supplying the engine cylinders.

The operation of the power plant shown in Figure 3 where the two circular: groups of engine cylinders are arranged in parallel relation. in

stead of in staggered relation as in Figures 4 and 8 will now be explained.

5| in opposite directions from the center towards the ends of this cylinder, as illustrated in Figure 12. Fins on the cylinder and on piston connector 36b (see Fig. 3) tend to radiate some of the heat from these cylinders into the compressed air atmosphere in the chamber 5|. As thesepistons separate, piston 61 impels link 83, causing it to move compressor cylinder II to the right as shown by the arrows in Fig. 12, and as this cylinder moves, its connecting rod it pulls the other cylinder 40 in the same direction to the right. Connecting rod 46 carries the rack bar II which meshes with fixed pinions 12 and 13 so these pinions are turned counter clock-wise, and as these pinlons meshalso with rack bar 10' carried by tube 31, this rack bar is moved in the opposite direction, to the left as shown in Fig. 3, thereby insuringsync-hronous movement of tube 3! in the same direction towards the left. However, the main propulsive force for causing this movement is coordinately produced by the piston rod 36b,

.since it is impelled towards the left by piston 85 ss'it moves outwardly and away from piston 6| in the firing or expansion stroke. As previously noted the piston rod 38b is connected to Injection of hot combustible gases or other fluid fuel will take'place in the narrow combus-j tion chamber between the closely contiguous ends of the pistons I5 and GI, Figs. 3 and 11. When these parts are thus positioned, pistons 62,-

have reached the limit of their expansion strokes the cam 85, (Fig. 9) on oscillating ring am has receded from a position under the roller Hit of rocker 84, while the cam 85 of the other oscillating ring Bic engaged roller tld of the rocker 84', and during the movement of this cam, the rocker has been tilted, causing poppetvalve Na in injector 83' to be pressed open, thereby ad mitting hot gasesfinto the combustion chamber between pistons and BI. Atthis time pop teeth Mon ring 8") has oscillated this ring in a pet valve Ola in injector 83 is closed under in-j direction to move cam 85 out or the rangeot rocker 84, by moving downwardly in cylinder 81a, which action causespiston 8'! on this rack bar to eject the oil or other fluid out of this cylinder into pipe C and it enters cylinder I05, as piston N therein is moved toward its extreme left'hand position. The pump 9| keeps up a constant cir. I culation of this oil or fluid in all the parts where same is needed, this excess oil delivered through pipe 0 being discharged to sump 92 through port v S in pipe D.-

While this is taking place, and ascompressor cylinder 4! also moves towards the left, piston N in cylinder 105a has, moved to its extreme left end position in this cylinder, thereby closingportj S in pipe-D and ejectingthe oil or other fluid- F outoi' cylinder mama) pipe 0' by-which it is conducted into cylinder 81b, causingthis oil as it rises in cylinder-81b to lift the piston 81' op-l erating therein. with the aidotthe pump pres-- sure, so that as piston 81' moves jupwardly, so does ring Ilc, causing its cam 85 to engage and trip rocker 84' into poppet-valve opening position.

and

the yoke 35 which is connected in turn to the tube 31 carrying the hollow pistons 38 and 39. The yoke also carries the rack bar 10 which, being responsive to forces imparted through the yoke or through the pinions I2 and I3, insures that the relative movements of the tube 31 and the connected compressor cylinders 40 and ll will be coordinated and synchronous.

"It, will be seen from Figure 3 that, be ore injection of fluid fuel occurs between contiguous pistons 35 and 6!, the ports 58 of their cylinder '33 are exposed for communication with air chamber. 51 through the interior of this cylinder at the rear of the advanced piston, these ports having just been uncovered by piston 61. As a consequence air at the pressure 01' the surround ing" atmosphere will fill the space 51. The quick outwardly-directed movement of this piston 61, when expansion of the gases takes place, first closes the ports 581and then successively uncovers the ports 56 and, 53, and finally reopens the ports #58las the piston 6l movesto the extreme right, 1v ,to a position corresponding to that of piston 62 8a'ses at the relatively high pressure obtaining in (the firing chamber will pass into the space 51 in- Fig. 3. When the extreme position is reached,

' causing the valvular members 55, a to slide lengthwise of the cylinders. 55

positions assumed by them at the end of the previous firing or expansion stroke of the pistons, 6| and which position is maintained until these pistons have reached the limit of their compression-strokeand the ports 58 have been again exposed, that at the right communicating with the g In Fig. 3 of the drawing the members .55, 55a are shown in the surrounding atmosphere and that at the left comthe resulting combustiongases exert a strong 7 municating with the firing chamber of cylinder I2". Owing to the diiference in pressure of the atmosphereand the gases in the firing chamber of cylinder 32', as the ports are uncovered and high pressure gases pass into the space 57 behind the valve SS-at the left of Fig. 3, they will urge the valves 55 and-55a, which are tied together by the link-5 9, to the right, thus establishing an outlet for the gases from the firing'chamber of the cyljinder 32' through port 56 and the opening G in va1ve]li 5 to,the discharge passage 54.

As the pistontl moves sufilciently to the right to open the ports 53, the opposing piston 35 moves 13 correspondingly to the left and eventually the piston 35 uncovers the air inlet ports 52. It will be observed, however, that the ports 52 and 53 are relatively so positioned with respect to the distances travelled by the opposing pistons that the discharge ports 53 will have partially opened before the air inlet ports 52 begin to become uncovered. This will insure that part of the combustion gases developed in the firing step shall have been permitted to discharge to the exhaust chamber 54 and that the pressure of the remaining gases will have been greatly reduced before the air inlet ports are opened and compressed air from chamber is permitted to pass into the cylinder through the ports 52. During the part of the outward stroke of the pistons 6| after the Ports 56 and 53 have been uncovered and until the piston approaches the extreme end of its stroke, the combustion gases are permitted to pass outwardly from the firing chamber through both the supplementary ports 56 and the main discharge ports 53 and during the latter part of this intermediate part of the stroke after the air inlet ports 52 have been uncovered, compressed air from the chamber 5| will fiow into the firing chamber displacing the combustion gases and thus perform the necessary scavenging operation. When the piston 6| passes to the end of the expansion stroke it finally uncovers the previously a covered port 58. At this instant, the corresponding port 58 at the left of the cylinder 32' will be uncovered by the piston 62 which is travelling to the right and thus the gases previously confined in the space 51 behind the valve 55 will be permitted to escape until atmospheric pressure is attained therein. At the same time gases at the pressure obtaining within the firing chamber of the cylinder 33' will enter the space 51 at the rearof the valve 55a and cause the latter to shift to the left, carrying with it the valve 55. In this way communication is established through the supplementary port 56 and the passage G in the valve 55a and this passage will remain open until the pistons 35 and GI have been brought to the limit of their compression stroke, as shown in Fig. 3,

whereupon the valves cated to the right.

It should be borne in mind that just after sleeve has thus been moved to the right, due to the 55 and 55a will be reciprouncovering of the port 58 and entry of compressed gases into space 51, piston 62 in cylinder 32' is also moving to the right, and as piston 6| which is sliding in cylinder 33' is covering ports 58 thereof piston 62 in cylinder 32' is sliding to the right therein covering progressively ports 58 and exhaust ports 53 and 58, and at the same time piston 34 of the same cylinder is approaching piston 62, and is covering airadmission ports 52 of this cylinder. During the portion of the compression stroke before the piston 34 completely closes the air inlet ports 52, compressed air supplied by the compressor cylinders to the chamber 5| will enter through the ports 52, sweep through the cylinder and out through the discharge ports 53, thereby exerting a cooling effect on the cylinder walls and the pistons. After the piston 62 completely closes exhaust ports 53 some of the compressed air previously admitted into cylinder 32' through ports 52, and which is being compressed by the approaching pistons 62 and 34, is now free to' emerge out of open ports 56, openings G in sleeve 55 and discharge chamber 54 to the inlet con nections of a turbine or other prime mover. As a result, all of the admitted air which would otherwise be subjected to a full compression stroke of the approaching pistons 82 and 34 and confined between them, is not allowed to be compressed and retained in the firing chamber. Accordingly while these pistons in cylinder 32' make afull expansion stroke, they make a restricted compression stroke in the sense that the amount of compressed air retained to partake in the flring of the fuel charge is reduced, and, therefore, the degree of heat that would otherwise be developed in the compression stroke is reduced. The same operation and effect of the pistons 62 and 84 are undergone bypistons 35 and 6| of cylinder 33' when it becomes their turn to make a compression stroke. In the latter event sleeve 55 will be restored, by means of the instrumentalities set forth, to the position it occupies in Figure 3, because, as pistons 62 and 34 approach the limits of their expansion stroke and piston 82 passes ports 58 of cylinder 32'. the gas in the chamber 51 at the left with which the port 58 registers is discharged, thus causing sleeve 55 to be moved back into chamber 51 to the left. As this takes place connecting rod 59 in moving to the left pulls sleeve 55a in cylinder 33 to the'left to the position it has in Figure 3.

As the pistons 38 and 38 approach the compressor cylinder walls which cooperate therewith, the air is compressed between them; and as the same pistons and walls of the compressor cylinders separate air is admitted between them. In Figure 12 it is seen that pistons 38 and 39 have changed their relative positions in cylinders 40 and 4| as illustrated in Figure 11. As these mobile elements are thus moving in the counter directions, cylinder 48 is impelling piston N of cylinder I85 towards the right therein, while cylinder 4| is pulling piston N of cylinder |05a also towards the right therein, but while piston N is ejecting the oil out of its cylinder, by way of pipe G into cylinder 81a, piston N is opening cylinder |05a for the admission of oil out of cylinder 81b by way of pipe CC. As the oil rises in cylinder 81:! it raises piston 81 therein, hence elevating the rack bar 88, which in turn engages the teeth M of ring 8| b and moves the ring upwardly, thus bringing cam 85 associated with this ring into the position shown in- Figure '12 where it engages rocker 84, trips or tilts it, causing poppet valve Na in injector 83 to open, just at the time pistons 62 and 34 of cylinder 32' have approached and define the constricted area or combustion chamber into which hot gases or other fluid fuel will be delivered from the injector. As this is taking place, and as piston N' moves'to the right in cylinder lll5a, the suction created in back pressure maintained by pump 8| induces oil to flow out of cylinder 81b into cylinder |05a.

Figure 9 shows a pinion liiTmou'nted on a fixed rod or shaft I08. which shaft is associated with a torsional volute spring coiled around it (not shown) with the effect that'when ring 8 lb or Me, as the case may be, has moved in one direction to retract its cam from engagement with its rocker 84, as a resultof rack bar 86 or 86' .of either cylinder 81a, 81b inwhing with the teeth of this ring, thev teeth Mof the'ring associated therewith, meshing also with pinion I01 will rotate it in a direction operative to wind up or tension the volute spring engaging shaft 18 of this pinion. It follows that this particular rackbar, say rack bar 85' of cylinder 81b of Figure 12, when resistance against its piston 81' is progressively being diminished dueto the oil F being withdrawn out of cylinder 81b, is reacted upon by ring 8|c which has been impelled by pinion I01 to of it, aided by 15 reverse its former direction of movement. because the torsional spring engaging its shaft I06 is now free to recoil and produce this reverse movement. Thereupon as ring 8 lo moves downwardly its teeth M, meshing with rack bar 86, impel this rack bar downwardly in cylinder 812; until it reaches the end of its movement in the bottom thereof, as shown inFigure 12. In this way the oil F has been transferred from cylinder 81b to cylinder I05a, and oil F has been transferred out of cylinder I05 to cylinder 81a. Pistons 35 and GI are now fully separated to the limit of their expensive stroke, and pistons 62 and 34 fully brought to the limit of their expansive stroke, so now another cycle of the engine takesplace in the manner already explained.

The compressed air of cylinders and H in Fig. 3 is driven out during the counter movements of these mobile assemblies by way of the ports 49 from within the hollow piston 38 and 39 into tube 31 from which it emerges into feeding-jacket i Under influence of compression of air between the pistons 38 or 39 and walls 42 or 45 of cylinder 40 or ll, as the case may be, valves 48 in pistons 30 and 39 open to discharge the compressed air, as just explained, into tube 31 while valves 41 remain closed. When the parts are moving in the direction where they come to rest at the extreme right of cylinders 40 and ll in Figure 11, this action is reversed. Now piston 39 and the opposite wall 44 of cylinder AI, and piston 38 and opposite wall 43 of cylinder 40 are approaching to compress air. Thereupon valves W of the pistons 38 and 39, which were previously closed during the stroke occasioned by separation of the particular pistons and cylinder walls just mentioned, now open, while valves 48 of these pistons previously open now close. Again the compressed air is ejected outthru the open ports 49 controlled by valves W and 48, into tube 31, thence being delivered to the firing cylinders.

It will be seen in Figure 3 that tube D has a leak or opening S so located that it will be uncovered by piston N of cylinder I05 when this piston isin its extreme left position in the cylinder. A similar opening S in the other tube D' is located in the same relative position in cylinder I05a as opening S is in cylinder I05, with relation to the piston N of cylinder I'll-5a when the latter piston occupies the same position in cylinder I05a that pistonN is shown to occupy in its cylinder 15.. But in the position of piston N actually shown in Figure 3, opening S of tube D is closed by the tubular portion P of such piston N, whereas opening S of tube D is un-' covered by piston N. g

It may sometimes happen that either of the tube pistons 38 or 39 willcome too close so as to collide with a wall of either compressor cylinder 40 or 4|. To prevent this I have provided shock absorbersas an optional feature of this invention. I have also provided means. for the elimination of'this hazard, of curtailing the pres,- sures in the particular compressor cylinder in which the affected piston operates.

' in this cylinder and air rushes into the cylinder The constantly operated pump 9| associated with each hydraulic cylinder I05 or I05a. is responsible for keeping the pressures in the coordinated cylinders, I05, 81a and mm, 81b adequate to sustain normal as'wellv as abnormal functioning of the machine shown in Figure 3. Reserve pressures are maintained in each of the fluid accumulators for constantly making an adjustable contribution of extrafluid where needed, under influence of the operating pump 9|, as well as of the regulator valve or cock 89.

The travel of the compressor cylinders, and consequent movements of the pistons N and 81, on the onehand, and N and 81' on the other hand is predetermined in accordance with definite pressure valves, valve 89 controlling the adjustment of fluid pressures to meet such valves,

while pump 9| and accumulator 90 furnish the' reserve pressure for this purpose. It follows that should the compressor cylinders and compressor pistons travel greater distances than they have been set in advance to traverse, an extra amount or liquid or oil will be forced into the appropriate one of the coordinated sets of cylinders as a result. Due to the presence of the safety ports S in the tubes D and D, when the compressor cylinders have stroked their utmost limits at either end of the machine, then that piston N or N, as the case may be, which has moved to its extreme left'position in cylinder I05will have uncovered ports S. Thereupon the increased amount of oil'that is being distributed into the space 16 of cylinder I05,'is allowed to by-pass out of ports S through tube D so that part of this oil is free to discharge and return to the sump or tank 92 where it is picked up by th'epump SI shown in Figure 10 it operates as follows. When tube piston 38, is moving to the right in cylinlder 40, while the cylinder is moving contrariwise, a suction is created which opens valves Y 40 through the space within the annular ring H. The air rushing through this space creates a suction in the pocket 99 connected by opening I00 with the said space provided by the ring H. This suction pressure in the pocket 99 effects movement toward the right in Fig. 10 of themember 90 having portions 980; projecting into the interior of the compressor cylinder 40. During the counter stroke towards the left of the piston 38, when the hazard exists that it might collide forcibly with cylinder head wall 96 of cylinder 40 when said head and piston 38 are approaching, it will be seen that air is compressed in the compression chamber between these movable parts, which action opens valves 48 of piston 38, but closes valves Y inwall 96 in this cylinder. when the plane surface of piston l8 draws very closeto wall 90 it will encounter the barrier of-fiange 98a of piston 98', thereby forcing this piston back tonormal position in its chamber, but under air resistance due to piston 98' compressing air in its chamber. This acts as a cushion which absorbs the shock of this stroke of the movable approaching parts by slightly slowing them down.

It will be seenin Figure 9 that fuel injection chamber 82 therein shown may be made to connect with oppositely arranged firing cylinders, so that each single fuel injector 83 may feed two same time. Thkwdevlce such cylinders at the may, if desired, be replaced by other mechanical arrangements and especially by approximately calibrated springs, lodged in recesses arranged in the thicknesses of the pistons or cylinder walls. l

From the foregoing it will be clear thatthe arrangement made for the compressors oi the machine is very compact; it reduces to a minimum the number of members to insure tightness, and on the other hand it secures perfect identity of the stressesby the gases on the homolothe adjacent ends and exhaust passages at their opposite ends, the fully separated pistons of one cylinder being located beyond the respective inlet and exhaust passages of their enclosing,

cylinder, while one of the contiguous pistons of the other aligned cylinder covers the exhaust passages thereof, each of said cylinders having auxiliary exhaust ports in advance of the exhaust passages covered by that piston "which has covered the exhaust passages, and means whereby as the approaching pistons near the center of their cylinder one of them will close the exhaust passages thereof as the exhaust passages of the other cylinder are uncovered, the auxiliary exhaust ports opening as the last mentioned exhaust passages are closing.

2. In an apparatus for generating and supplying heated and compressed gases to a gas turbine or other prime mover, in combination, internal combustion cylinders arranged in axial alignment, a pair of opposed pistons in each cylinder, compressor cylinders having links attached to the outer-end pistons of such cylinders for joint movement therewith, compressor 18 having inlet and exhaust es uncovered by the separated pistons, and auxiliary exhaust parts which are closed in the mentioned'positions of both sets 0! pistons, the separated pistons approaching each other .as the compressor pistons reverse their positions in the-compressor cylinders to close the inlet and exhaust passages, while the other pistons separate, and

means actuated by one ofthe separating pistons to close its auxiliary exhaust ports while one of the approaching pistons covers its exhaust passages, and means whereby the auxiliary exhaust ports are automatically opened to the path of movement of the approaching pistons.

, 3. In an apparatus for generating and supplying heated and compressed gases to a gas turbine or other prime mover, in combination,

0ppositely movable interacting compressor elements, internal combustion engine cylinders having opposed pistons therein, said cylinders having at opposite ends exhaust and inlet passages, and in advance of said exhaust passages auxiliary exhaust ports, a slidable sleeve on said cylinder having an opening designed to register with said exhaust passages and exhaust ports collectively or separately and means causing said sleeve to act in time with said pistons, whereby said sleeve covers said exhaust ports except when pistons in said compressor cylinders connected one of said pistons closes the exhaust passages when it moves to uncover these ports to permit I the other piston to expel exhaust out of these ports.

PIERRE ERNEST MERCIER. ERNEST FREDERIC MERCIER.

file of this patent:

UNITED STATES PATENTS Number Name Date a 658,367 Haynes et al Sept. 25, 1900 995,857 Ful'lagar June'30, 1911 1,174,560 Fullagar Mar. 7, 1916 1,514,476 Still Nov. '4, 1924 1,930,786 Witkiewicz et al. Oct. 17, 1933 1,950,063 Pescara Mar. 6, 1934 2,090,709 Steiner Aug. 24, 1937 2,115,921 Steiner May 3, 1938 2,132,083 Pescara Oct. 4, 1938 2,139,425 Steiner Dec. 6, 1,938 2,159,197 vBarra-Frauenfelder May 23, 1939 2,222,260 Janicke Nov. 19, 1940 2,241,957 Pescara May 13, 1941 l9 p x 20 Certificate of Correction. Patent No. 2,466,255 3 1 April 5, 1949 -ERNEST FREDERIC. 'MERCIER ET AL;

It is hereby certified that errors appear in the printed specification of the above numbered patent requiring correction as follows:

Column 4, lines 71 and 72, strike out the word device; column 9, line 7, strike out rod and insert the same after piston, line 8; line 30, strike out rod and insert the, same after piston, line 31; column 10, line 2, for are making read thus make; line 3, for thus make read are making; line 70, for out of read from;

line 71, for from read out of; column 14, lines 65, 66, and 67, for eof this ring, the

teeth M of the ring associated therewith read of the rack associated therewith, the teeth M of this ring column 16, lines 65 and 68, for 98' read 98;

and that the said Letters Patent should be read with these corrections therein that the same may conform to the record of the case in the Patent Oflice.

Signed and sealed this 10th day of January, A. D. 1950.

'rnoms F. MURigHY,

Assistant Uommz'asioner of Patents. 

